Fluid pump or motor with geared roller abutments



July 12, 1966 G. w. BRAND E 3,260,166

FLUID PUMP OR MOTOR WITH GEARED ROLLER ABUTMENTS Filed March 9, 1964 5 Sheets-Sheet 1 NroRs:

PHILIP HARTMANN LBERT SCHMITZ July 12, 1966 cs. w. BRAND ET AL 3,260,166

FLUID PUMP OR MOTOR WITH GEARED ROLLER ABUTMENTS Filed March 9. 1964 5 Sheets-Sheet 5 FIG. 3 7/ GEORGE BRAND 3 PHILIP HARTMANN By: ALBERT SCHMITZ 43 5 A T TORNEY July 12, 1966 G. W. BRAND ET AL FLUID PUMP OR MOTOR WITH GEARED ROLLER ABUTMENTS 5 Sheets-Sheet 4 Filed March 9, 1964 lA/vg/vro/Ps: GEORGE BRAND PHILIP HARTMAM I ALBERT SCHMITZ w- JWmA 7' TOR/V5) July 12, 1966 G. w. BRAND ET L 3,260,166

ID M OR B I/Vl EN 7'OR5-' 6E0 E BRAND PHIL ARTMANN BK 2:85;; ZCHMITZ A 7'7'ORNEV United States Patent "ice 3,260,166 FLUID PUMP 0R MOTOR WITH GEARED ROLLER ABUTMENTS George W. Brand, Philip Hartmann, and Albert A.

Schmitz, Racine, Wis., assignors to Hartmann Manufacturing Company, Racine, Wis., a corporation of Wisconsin Filed Mar. 9, 1964, Ser. No. 350,943 Claims. (Cl. 9182) This invention relates to a fluid pump or motor with geared roller abutmen'ts, and more particularly, it relates to a hydraulic motor for receiving fluid pressure and converting it into rotary motion. This is a continuationin-part of US. patent application Serial No. 280,611, filed May 15, 1963, and now abandoned.

It is an object of this invention to provide an efficient and generally improved fluid pump or motor unit, or hydraulic motor, for converting fluid pressure into rotary motion.

Another object of this invention is to provide a fluid pump or motor unit wherein fluid pressure is utilized for producing rotary motion within the unit which is arranged to fluid-tightly control the pressure therein for maximum efficiency, and yet have the unit subjected to only a minimum of frictional forces, and with the unit being of a minimum of complexity for manufacturing.

Still another object of this invention is to provide a fluid pump or motor unit which produces a high torque through a relatively small size unit which also produces a high speed when it is desired. This particular object is accomplished by providing control means which direct the fluid pressure to the working parts of the unit for either the high torque or the high speed desired, in selective options.

. Still another object of this invention is to provide a fluid pump or motor unit wherein the parts which are exposed to the fluid pressure are fluid tightly arranged to preclude leakage of fluid, and the fluid itself is applied in both the fluid sealing and the incidental movement of the parts in the operation of the unit.

Another object of this invention is to provide a fluid pump or motor unit of a stator and rotor type for utilizing hydraulic pressure to produce rotary motion, and with the unit being highly eflicient in that it is fluid tight, particularly through the utilization of gear teeth between the rotating parts, and also the teeth being available to permit variable radial positioning between the parts, but nevertheless maintain the fluid-tight relationship by virtue of the provision of gear teeth.

This unit also utilizes rollers and a stator meshed together with the rollers spaced around the stator and having cut-outs to receive vanes on the stator. The object here is to have the roller gear teeth fluid sealed simultaneously at the roller bore and the stator to avoid fluid slip.

This particular invention has found particular application in mobilizing vehicles, such as automobiles and trucks, by providing the vehicle wheel hub with one part of the unit, and providing the vehicle axle with the other part of the unit, and directing the fluid pressure between the two parts to create the necessary rotation of the hub. Also, in connection with this application, the alternate high torque, and high speed conditions can be achieved as desired in a vehicle, and also even reverse direction of movement can be accomplished, and all of these features are accomplished by control of the direction of flow of the hydraulic fluid. Accordingly, this is an object of the invention and it will be described in connection with the application to the vehicles.

Other objects and advantages will become apparent 3,260,166 Patented July 12, 1966 upon reading the following description inlight of the accompanying drawings wherein:

FIG. 1 is a sectional view of a preferred embodiment of this invention and showing a fragment thereof broken away and also showing a fragment of a vehicle rim or hub, and with the section taken along the line 11 of FIG. 2.

FIG. 2 is a sectional view taken on the line 22 of FIG. 1 and with a fragment thereof broken away.

FIG. 3 is a sectional view of a continuation of the embodiment shown in FIG. 1 and showing the control and fluid passageways, and with the section taken along the line 3-3 of FIG. 4.

FIG. 4 is an end elevational view of that shown in FIG. 3 with a fragment thereof broken away.

FIGS. 5, 6, 7, and 8 are sectional views of parts shown in FIG. 2, but with the center part thereof shown in different operating positions,

FIG. 9 is a sectional view similar to FIG. 7, with a part thereof altered to present a modification.

FIG. 10 is a fragmentary sectional view taken on the line 10-10 of FIG. 1 but showing the unit in an advanced position from that of FIG. 2.

The embodiment shown in the drawings consists generally of an outer member or rotor 10, and an inner member or stator 11. These parts respectively can represent the hub of a vehicle wheel and the axle of a vehicle wheel, and it will be further noted that a fragment of a vehicle rim 12 is shown mounted on the rotor 10, and it would of course be understood that these parts are all axially aligned with respect to a wheel in a conventional and obvious manner. Thus, as shown in FIGS. 1 and 2, the stator 11 is stationarily mounted, while the rotor 10 is supported thereon by means of the bearings 13 and 14 to be rotatable thereover. The rotor 10 includes side pieces 16 and 17 and center piece 18. Also, end plates 19 and 21 are included in the rotor 10, and these pieces are all secured together by means of the bolts 22 shown in FIG. 2. A fluid seal 23 is disposed between the rotor 10 and the stator 11 to prevent fluid leaking therepast.

The rotor parts have openings 24 extending therethrough for rotatably receiving rollers 26. Thus, bearings 27 are disposed within the openings 24, and it will of course be understood that the opposite ends 28 of the rollers 26 are rotatably mounted in the rotor pieces 16 and 17. Thus, the roller intermediate or center portion 29 is disposed to extend through the length of the opening 24 in the rotor center piece 18.

FIG. 2 shows that the rotor has a circular wall 31, and the opening 24 intersects the wall 31 so that the roller portion 29 extends through and radially inwardly of the wall 31 as shown in FIG. 2.

The stator 11 also has a central portion 32, and this is shown to be coextensive, or of equal length, with the roller intermediate length 29. Again FIG. 2 shows the stator portion 32 to have a gear pitch circle designated 33 which is spaced from the rotor wall 31 so that the two define an annular space therebetween, and this is the working chamber of the unit. The length of the working chamber is of course the length of the rotor centerpiece 18, and the working chamber is designated 34. Thus the roller intermediate portions 29 extend beyond the working chamber 34, and the side pieces 16 and 17 define the length of the working chamber by their faces 36 and 37, respectively, and these side pieces have a counterbore 38 for fluid tightly receiving the stator central portion 32.

It will also be noted that the stator has vanes 39 extending radially thereon through the working chamber 34 so that the arcuate outer surfaces 41 of the vanes conform to and are fluid tight with the bore wall 31 of the rotor. FIG. 1 shows the width of the vanes 39, and it will of course also be understood that the faces 36 and 37 of the pieces 16 and 17 are overlapping and fluid tight with the sides of the vanes 39. Still further it will be noted in FIG. 2 that the length of the vanes 39 along the wall 31 is sufficient to span the openings 24 so that fluid cannot leak nor flow from one side of the opening 24 to the other side when the vane is positioned thereover as shown at the top of FIG. 2.

The stator piece 32 and the roller intermediate portions 29 have spur gear teeth 42 and 43 respectively on their circumferences. These teeth are of course in constant mesh as they extend continuously around both the stator and each of the rollers 26, and this therefore keeps the rollers in synchronization with the stator with respect to the vanes 39 since it will be noted that the rollers have curved or relieved portions 44 which pass over the vane surfaces 41, and this is in a fluid-tight rolling contact between the surfaces 41 and 44. Roller cut-outs or pockets 45 are provided for receiving the values 39. The ratio of rollers 26 to vanes 39 is two to one.

FIG. 2, particularly, shows that the teeth 42 and 43 provide a fluid-tight seal therebetween for the desired purpose of retaining the fluid presure which of course induces the rotation in the rotor 10. Thus fluid pressure indicated P in FIG. 2 can be assumed to be in the area shown, and this will of course be sealed off along the line 46 where the two teeth are meshing, and thus the pressure cannot go beyond that point. Also, the presure will be acting on that roller 26 downwardly and to the left as viewed in FIG. 2, and thus the pressure will induce rotation of the rotor in the direction indicated by the arrow A since the stator 11 can be held in a fixed position by means not shown. Still further, the fluid pressure P will exert an uncountered force designated B upwardly on the roller tooth as indicated, and this will induce the roller to rotate in the direction indicated C, as desired. Therefore, it will be noted that the fluid pressure induces both the rotor rotation and it further assists in rotating the roller in the direction of rolling relationship with the stator, as desired. Of course the force on the roller induced by the force designated B is not countered by any force because of the contact line 46 and the balanced pressure between all other teeth. It will of course also be understood that the stator teeth 42 extend throughout the length of the piece 32, and this is of course coextensive with the roller teeth 43, except for the portions of both the stator and the roller where the vanes 39 and the cut-outs 45 are located as shown in FIG. 1. Thus it will be actually understood that the stator can be formed by having its teeth 42 formed entirely around, and for the length of, the piece 32, and then the vanes 39 can have ring teeth formed therein so that the vanes can simply be disposed directly over and in keyed relationship with the teeth 42 on the stator, as shown.

Similarly, the rollers 26 have the teeth formed entirely therearound and for the length of the intermediate portions 29, and then the cut-outs 45 can be formed in the rollers.

With the provision of the teeth 42 and 43, it will now be seen that the rollers 26 can be mounted in the rotor with the bearings 27, and the fit between the stator and the rollers need not be precise to have virtually complete fluid sealing therebetween. That is, the teeth 42 and 43 can move toward or away from each other within of course the tolerances of their meshing relation, and they will still maintain a fluid seal therebetween because of the nature of the spur type of gear teeth shown. This therefore provides for easy manufacture and interchangeability of parts from one unit to another, since each unit is Virtually self-adjusting and yet self-sealing because of the gear teeth feature mentioned.

The stator 11 also includes the elongated portion 47 which is secured to the portion 32 by the key 48. Fluid passageways 49, 51, 52, 53, 54 and 56 are provided in the stator 11 with the passageway extending through opposite sides of the vanes 39 as shown. These passageways are in fluid-flow communication with an opening or bore 57 in the member 47. Also it will be noted that a valve 58 is disposed within the bore 57 to be rotatable therein, and the valve has gates 59, 6t), 61, 63 and 64 projecting therefrom into fluid-tight contact with the bore 57. Still further, the valve has fluid ports 66, 67 and 68 extending from a central bore 69. It will further be recognized that the vanes fluid seal each of the three ports from the other with respect to the bore 57, at least in the position shown in FIG. 2.

FIG. 3 shows the end of the member 47, and the ports which communicate with the bore 69 are in common fluid communication with a fluid inlet 71 in a housing 72 surrounding the member 47 and secured thereto by a key 73. Thus a fluid supply line can be connected to the opening 71 and inlet fluid, for instance, can be applied to the bore 69 to create inlet pressure in the valve port and in the chambers between the valve vanes decribed. Of course if the chambers are in flow communication with the stator pasageways 49-56, then the inlet pressure is applied to the working chamber of the unit.

FIG. 3 also shows that the bore 57 connects through the housing 72 to a fluid pasageway 74 which has a fluid outlet in a boss designated 75, the same as the boss 89 has its outlet 71. In this manner, passageway 57 and the passageway 69 are normally separated from each other, and it will of course be understood that the bore 57 defines the three passageways 76, 77 and 78, which are fluidseparated from the valve ports and the passageway 69.

A further passageway 79 is provided in the member 47 by means of a tubular member 81, and this passageway 79 provides for drainage of slip oil or the like through the passageway 82 and the housing outlet 83.

An end cap 84 is provided at the end of the housing 72 and is secured to the member 47 by means of the set screws 86. A shift lever 87 is pivoted on the cap 84 through a pin 88, and a lug 89 on the lever 87 engages a slot 91 in the housing 72. It will therefore be understood that upon pivoting the lever 87, its lug 89 can be withdrawn from a locked position with the housing 72, and the cap 84 receives the lever 87 in a slot 92 so that rotation of the lever 87 will also rotate the cap 84' and likewise rotate the member 58. Additional notches 93, 94, and the like are provided in the housing 72 for selective setting of the lever 87 and rotation of the valve 58, for a purpose described later. A spring 96 is provided for re taining the lever 87 in a locked position with respect to the selected one of the notches described.

With respect to the positioning of the valve 58 and the pressurizing of the working chamber 34, it will be noted in FIG. 2, for instance, that if fluid pressure is applied through the opening 71 and into the passageway 69, then it will of course go through the ports 66, 67, and 68, and into the passageways 51, 53, and 56. This pressure will be eflective on the rollers 26 which are respectively immediately clockwise from the three passageways mentioned, and this will therefore induce the rotor 10 to rotate in a clockwise direction. Of course the vanes 39 prevent the fluid from passing counterclockwise beyond the vanes, and thus the fluid pressure can be effective for the rotation mentioned. In this position of valve operation, the passageways 49, 52, and 54 serve to receive the outlet fluid and conduct it into the passageways 76, 77, and 78 and out the outlet passage mentioned, at 75. In this manner, all of the rollers and all of the three vanes 39 are effective to utilize the fluid pressure and rotate the rotor 10.

Therefore, the rotor 10 can be rotated in either direction, and also only selected ones or one of the rollers 26 can have the fluid pressure applied against it by means of manipulation of the valve 58. This therefore gives complete control of both torque and speed and forward or reverse direction of rotation.

Still further, the passageways and the ports and the valve vanes described are all arranged so that the fluid pressure can be best applied, including the application of the pressure during the transition from one position described to another position; that is, FIG. 5, for instance, shows the valve rotated slightly clockwise from the FIG. 2 position, and at this position, the pressure applied, for instance, in the port 68, would be released directly through the outlet through the passageway 56 and the outlet 76, and thus there is a desirable transition or midpoint in the shifting operation where there is no high fluid pressure which could conceivably damage parts.

FIG. 6 shows the position of the valve 58 so that only two of the rollers 26 are in an operative position. Thus, fluid pressure in the bore 69 communicates with the passageway 53 through the port 67, and likewise it communicates with the passageway '51 through the port 66. In these instances, the passageways 52 and 54 respectively are utilized as return flow passageways. Thus the two stator vanes 39 at the lower portion of FIG. 2 are effective for the operation described.

In the FIG. 7 position the valve 58 is in a neutral position since none of the vanes and rollers can be pressurized by the fluid because of the position and relationship between the valve and the stator. This of course is therefore a neutral position with respect to the drive of the rotor.

FIG. 8 shows a valve position wherein the three vanes 39 of the stator are effective for operation, but this position induces rotation reverse to the rotation induced by the valve position in FIG. 2. Here it will of course be seen that pressure in the passageway 69 extends through the ports 66, 67, and 68 and into the passageways 52, 54, and 49 respectively. This therefore applies fluid pressure to one side of the three vanes 39 to induce the rotation mentioned.

FIG. 9 shows a modification of the embodiment shown, for instance in FIG. 7. It will here be noted that the valve is provided with vanes 96, 97, 98, 99, 101, and 102, which are sufficiently dimensioned to cover the passageways 49 and the like, and therefore block flow through the passageways. With the FIG. 9 embodiment and with the valve set in the position shown in FIG. 9, it will then be understood that this provides a brake or precludes rotation of the rotor with respect to the stator since fluid cannot flow through the passageways. It will therefore be apparent that where this type of stop or brake arrange ment is desired, then the valve 58 can be modified to simply provide the enlarged vanes as shown.

Thus the advantages of this unit are the provision of a gear seal between the rotor and the stator with their respective teeth 43 and 42. These elements can of course move radially away or toward each other and still retain their seal because of the nature of the gear teeth. Also the torque and the speed can be varied by the manipulation of the valve 58. Of course the rotor can also be reversed in its direction of rotation. Still further, the fluid pressure applied in the working chamber will actually assist the rotation of the rollers 26 by virtue of the pressure indicated by arrow B which tends to rotate the roller in the desired direction.

FIG. 10 particularly indicates the function of the gear teeth 42 and 43 to remain fluid tight with each other and with the gear teeth 43 being fluid tight in the bores 24 that is hereinafter described. The valve 58 is set to have passageway 51 as the inlet so when the inlet 51 is between the two rollers fluid pressure indicated P is of course effective against the two adjacent rollers 26, and it urges the rollers away from each other. When the rotor moves so the passageway 51 is in the FIG. 10 position, the gear tooth designated 103 is fluid tight with the bore 24, and the teeth 42 and 43 are fluid tight at a point indicated 104 and at still another point indicated 105. Thus the fluid pressure cannot pass from the chamber indicated and beyond the two rollers shown either by passing between the teeth 42 and 43 or around the rollers 26 and through the bores 24.

Therefore, with the rotor 10 rotating in the direction of the arrow A, and with the rollers 26 rotating in the directions of the arrows C, the tooth 103 still fluid seals between the upper roller 26 and the wall defining the roller bore 24 when the roller tooth 107 is moved to a position where the fluid-tight line indicated is established.

Thus the cut-outs 45 in the rollers 26, and the extent of the teeth 43 on the roller 26, are such that the rollers are both in mesh with the teeth 42 of the stator 11 at the time that roller tooth 103 is also sealing with the wall 24 to avoid passage of fluid between the inlet and outlet passageways at the moment of transition between the time that the inlet passageway is sealed and the time that it is opened to certain sections of the working chamber 34. The length of the gear teeth on the rollers is sufficient so the tooth 103 is adjacent the working chamber and is located less than 180 degrees around the roller and on the side opposite from the chamber with pressure P, at the time that the two adjacent rollers are in mesh with the teeth 42. In fact, the tooth 103 is in the roller bore 24 at the intersection with the working chamber when there is meshing at points 104 and 105, and tooth 103 is shown located less than 90 degrees from the sealing teeth at 104.

Roller bores 24 are fully enclosed by the rotor 10, as shown in FIG. 1, so fluid leakage will be no problem. Thus, sleeve type of fluid seals 108 are pressed onto the roller ends 28 and have circular sealing surfaces 109 with the bores 24. Any fluid slipping past the seals 109 to one end of the roller 26 can also get to the other end of the roller by the fluid passageway 110 extending throughout the length of each roller 26. The rollers are thus fluid balanced axially. The enclosed rollers improve eificiency by eliminating slip.

What is claimed is:

1. A fluid motor comprising an inner member and an outer member arranged with an annular space therebetween and said members being relatively rotatable, one of said members having bores therein spaced therearound, rollers rotatably mounted in said bores on said one of said members and extending through said annular space, the other of said members and said rollers both having gear teeth disposed therearound in meshing and fluid-sealing relation across the axial length of said annular space, vanes radially extending on said other of said members in spaced relation therearound and through said annular space and being in fluid-sealing relation with said one of said members, said gear teeth on each of said rollers extending only partly therearound for a selected length of the circumference and with each of said rollers having a pocket therein in the remainder of said circumference for receiving said vanes upon relative rotation of said members, said other of said members having only one fluid inlet passageway and only one fluid outlet passageway for each of said vanes and extending on opposite sides of each of said vanes and extending through said other of said members to the exterior of said motor, said selected length of said gear teeth, and the number and location and length of each of said vanes, and the size of each of said pockets, all being sufficient to have one of said rollers fluid seal with said gear teeth on said other of said members and with one of said members in said bore at a location adjacent said annular space and to the side of said one roller in the direction of rotation of said one member until the one of said rollers, adjacent said one roller in the direction opposite said direction of rotation, simultaneously receives one of said vanes in said pocket and makes its fluid seal with said gear teeth on said other of said members.

2. A fluid pump or motor comprising an inner member and an outer member arranged with an annular space therebetween and said members being relatively rotatable, one of said members having bores therein contiguous to said annular space and spaced therearound, roller rotatably mounted in said bores on said one of said members and extending through said annular space, the other of said members and said rollers both having gear teeth disposed therearound in meshing and fluid-sealing relation across the entire axial length of said annular space, vanes radially extending on said other of said members in spaced relation therearound and through said annular space and being in fluid-sealing relation with said one of said members and being of a length sufficient to span said bores and being of a width less than and intermediate said axial length of said annular space, said gear teeth on each of said rollers extending only partly therearound and with each of said rollers having at least one pocket therein in the remainder of said circumference and dimensioned to snugly receive said vanes upon relative rotation of said members, said other of said members having only one fluid inlet passageway and only one fluid outlet passageway for each of said vanes and extending on opposite sides of each of said vanes and extending through said other of said members to the exterior of said pump or motor, said gear teeth on said rollers being located, and said vanes being arranged, to have one of said rollers form a fluid seal with said gear teeth on said other of said members and also with one of said members in said bore at the intersection of said bore and said annular space at one side of said one roller until an adjacent one of said rollers opposite said one side simultaneously receives one or" said vanes in said pocket and makes its fluid seal with said gear teeth on said other of said members.

3. A fluid motor comprising an inner member and an outer member arranged With an annular space therebetween and said members being relatively rotatable, one of said members having bores therein contiguous to said annular space and spaced therearound, rollers rotatably mounted in said bores on said one of said members and extending through said annular space, the other of said members and said rollers both having gear teeth disposed therearound in meshing and fluid-sealing relation across the entire axial length of said annular space, vanes radially extending on said other of said members in spaced relation therearound and through said annular space and being in fluid-sealing relation with said one of said members and being of a length suificient to span said bores and being of a width less than and intermediate said axial length of said annular space, said gear teeth on each of said rollers extending only partly therearound for a selected length of the circumference and with each of said rollers having a pocket therein in the remainder of said circumference and dimensioned to snugly receive said vanes upon relative rotation of said members, said other of said members having only one fluid inlet passageway and only one fluid outlet passageway for each of said vanes and extending on opposite sides of each of said vanes and extending through said other of said members to the exterior of said motor, valve means in said other of said members and having a fluid inlet port and a fluid outlet port in separate flow communication with certain of said passageways, and said valve means being shiftable and having its said ports disposed to fluid-flow communicate with selected ones of said passageways for fluid pressurizing selected ones of said rollers and for reversing relative rotation of said members, said selected length of said gear teeth, and said vanes being arranged, to be sufficient to have one of said rollers fluid seal with said gear teeth on said other of said members and with one of said members in said bore at a location adjacent said annular space until an adjacent one of said rollers simultaneously receives one of said vanes in said pocket and makes its fluid seal with said gear teeth on said other of said members.

4. A fluid pump or motor comprising an inner member and an outer member arranged with an annular space therebetween and said members being relatively rotatable, one of said members having bores therein spaced therearound and defined by circular walls, rollers rotatably mounted in said bores and extending through said annular space, the other of said members and said rollers having gear teeth in meshing and fluid-sealing relation across the axial length of said annular space, vanes radially etxending on said other of said members in spaced relation therearound and through said annular space and being in fluid-sealing relation with said one of said members, said vanes being of a length suflicient to span said bores, the ratio of said rollers to said vanes being two to one, said other of said members having only one fluid inlet passageway and only one fluid outlet passageway for each of said vanes and extending on opposite sides of each of said vanes, each of said rollers having -a pocket interrupting said gear teeth on said rollers for receiving said vanes upon relative rotation of said members, the size of said pocket around the circumference of each of said rollers and the remaining length of said gear teeth on each of said rollers being suflicient to have certain ones of said gear teeth of two adjacent rollers in mesh with said gear'teeth of said other of said members, for forming a fluid-tight chamber along the portion of said annular space intermediate said rollers, and with said chamber being defined by the pitch diameter of said other of said members, at the same time that other ones of said gear teeth of both of said two adjacent rollers are on said walls of said bores at their respective points adjacent said annular space and located less than degrees around said rollers to the sides of said rollers opposite from said fluid-tight chamber to have said other ones of said gear teeth of said two adjacent rollers fluid tight with said Walls.

5. A fluid pump or motor comprising an inner member and an outer member arranged with an annular space therebetween and said members being relatively rotatable, said outer member having bores therein spaced therearound and defined by circular walls, rollers rotatably mounted in said bores and extending through said annular space, said inner member and said rollers having gear teeth in meshing and fluid-sealing relation across the axial length of said annular space, vanes radially extending on said inner member in spaced relation therearound and through said annular space and being in fluid-sealing relation with said outer member, said vanes being of a length sufiieient to span said bores, the ratio of said rollers to said vanes being two to one, said inner member having only one fluid inlet passageway and only one fluid outlet passageway for each of said vanes and extending on opposite sides of each of said vanes, each of said rollers having a pocket interrupting said gear teeth on said rollers for receiving said vanes upon relative rotation of said members, the size of said pocket around the circumference of said roller, and the remaining length of said gear teeth on each of said rollers, and said length of said vanes, all being arranged such that, when one of said vanes is disposed in said pocket of one of said rollers, said gear teeth of said one of said rollers and another of said rollers adjacent said one of said rollers are in mesh with said gear teeth of said inner member for forming a fluid-tight chamber intermediate the two said rollers at the same time that said gear teeth of said another of said rollers extend continuously from the point of meh with said inner member and around said roller in a direction away from said chamber and to a location on said wall of said bore to be fluid tight with said wall.

References Cited by the Examiner UNITED STATES PATENTS 813,854 2/1-906 Burlich 9l92 821,707 5/1906 Dawe 9l92 X (Gther references on following page) 9 UNITED STATES PATENTS Met-calf et a1. 91-92 Keene 919'2 X Ogden 9192 Mau 9192 Whitfield 2 30-450 Doe et a1. 60-53 X Hofiar 9192 X Skok 91- 92 Taylor 103-4125 Hartmann 103--12 5 10 FOREIGN PATENTS 8,200 1909 Great Britain. 376,162 7/ 1932 Great Britain.

445 ,072 4/1936 Great Britain.

5 602,836 6/194-8 Great Britain. 643,937 9/1950 Great Britain.

79,657 11/ 1931 Sweden.

MARK NEWMAN, Primary Examiner.

SAMUEL LEVI'NE, Examiner.

A. S. ROSEN, Assistant Examiner. 

1. A FLUID MOTOR COMPRISING AN INNER MEMBER AND AN OUTER MEMBER ARRANGED WITH AN ANNULAR SPACE THEREBETWEEN AND SAID MEMBERS BEING RELATIVELY ROTATABLE, ONE OF SAID MEMBERS HAVING BORES THEREIN SPACED THEREAROUND, ROLLERS ROTATABLY MOUNTED IN SAID BORES ON SAID ONE OF SAID MEMBERS AND EXTENDING THROUGH SAID ANNULAR SPACE, THE OTHER OF SAID MEMBERS AND SAID ROLLERS BOTH HAVING GEAR TEETH DISPOSED THEREAROUND IN MESHING AND FLUID-SEALING RELATION ACROSS THE AXIAL LENGTH OF SAID ANNULAR SPACE, VANES RADIALLY EXTENDING ON SAID OTHER OF SAID MEMBERS IN SPACED RELATION THEREAROUND AND THROUGH SAID ANNULAR SPACE AND BEING IN FLUID-SEALING RELATION WITH SAID ONE OF SAID MEMBERS, SAID GEAR TEETH ON EACH OF SAID ROLLERS EXTENDING ONLY PARTLY THEREAROUND FOR A SELECTED LENGTH OF THE CIRCUMFERENCE AND WITH EACH OF SAID ROLLERS HAVING A POCKET THEREIN IN THE REMAINDER OF SAID CIRCUMFERENCE FOR RECEIVING SAID VANES UPON RELATIVE ROTATION OF SAID MEMBERS, SAID OTHER OF SAID MEMBERS HAVING ONLY ONE FLUID INLET PASSAGEWAY AND ONLY ONE FLUID OUTLET PASSAGEWAY FOR EACH OF SAID VANES AND EXTENDING ON OPPOSITE SIDES OF 